Mold closing boost mechanism for glassware forming machine



Aug. l2,v 1969 G. E. Rows 3,460,931

MOLD CLOSING BOOST MECHANISM FOR GLASSWARE FORMING MACHINE Filed DBC. 29, 1966 2 Sheets-Sheet l Aug. 12, 1969 G. E. RowE 3,460,931

MOLD CLOSING BOOST MECHANISM FOR GLASSWARE FORMING MACHINE Filed Deo. 29, 1966 2 Sheets-Sheet 2 United States Patent O U.S. Cl. 65-313 8 Claims ABSTRACT OF THE DISCLOSURE A pair of piston type pneumatic motors are mounted close to two mold holder arms for forcibly engaging the knee portions of a pair of toggle links, which pivotally move said arms, to boost said links during their closing movement. An antideiiection bracket or tie bar is also provided for stilfening the mold hinge pin upon which the mold holder arms are pivotally supported.

BACKGROUND OF INVENTION A glassware forming machine of the Hartford I S. type, disclosed in Patent No. 1,911,119 to Ingle, utilizes a pair of driven rock shafts alongside the mold hinge pin for moving the mold holder arms through a pair of toggle links connecting the upper ends of each of said shafts to its associated mold holder arm. The rock shafts are quite long and are driven from their ,lower ends by a complex linkage system which is adequately disclosed in the aforementioned patent. While the means shown in the Ingle patent for driving the shafts has proven satisfactory in the past for the forming of most glassware, it has been found that with the higher speed operations necessitated by present day requirements, especially in the forming of relatively large ware, excessive deflections of the hinge pin have been encountered during closing of the mold sections. In addition, the complex linkage system which imparts pivotal motion to the mold holder arms suffers from internal friction in its many joints, as well as from deflections of its various component links. As a result of these deficiencies the closing force achieved at the mold is often substantially below the force desired.

SUMMARY OF 'TI-IE INVENTION In the device disclosed here, an anti-deflection bracket and support post are provided adjacent the hinge pin, and a pair of uid motors are mounted on either side of said post to provide additional force to the mold closing mechanism adjacent to the mold itself, and more particularly to forcibly engage the knee portions of each of the toggle links used to connect each of the mold holder arms to its associated rock shaft.

It is the general object of the present invention to provide a more rigid hinge pia for the mold holder arms of the glassware forming machine so that additional force can be applied to the linkage for moving the mold sections especially during closing movement thereof.

BRIEF DESCRIPTION OF THE DRAWINGS FIGURE l is a plan view of the blank mold side of a typical Hartford I.S. machine section, and shows the conventional hinge pin, the mold sections, the mold holder arms to which said sections are attached, the toggle links for connecting each of said arms to an associated driven rock shaft, and an antideflection bracket and its associated pneumatic motors of the present invention with one of the latter being shown in section.

FIGURE 2 is a side elevational view of the apparatus shown in FIG. 1 with certain other parts of the glassware forming machine section being added in schematic fashion.

3,460,931 Patented Aug. 12, 1969 FIGURE 3 is an enlarged horizontal section showing one end of the anti-deflection bracket or tie bar, being taken along the line 3-3 of FIGURE 2.

FIGURE 4 is a similarly enlarged vertical section showing the opposite end of the anti-deflection bracket or tie bar, being taken along the line 4-4 of FIGURE 1.

FIGURE 5 is a further enlarged vertical sectional view of an exhaust valve provided in the air pressure manifold to the pneumatic motors, being taken along the line 5-5 of FIGURE 1.

DETAILED DESCRIPTION Turning now to the drawings in greater detail, FIG. 1 shows a blank mold of the double gob variety, comprising two partible mold sections 10a and 10b, each of which is secured to an associated mold holder insert, 12 and 14 respectively, by conventional means. The inserts 12 and 14 are pivotally carried on mold holder arms 2i? and 22, respectively, each of which is movable between the positions shown in full and broken lines in response to angular movement of its associated rock shaft 24 or 26, as indicated by the arrows 28 and 30. The inserts are held to their associated arms 2G and 22 by pins 21 and 23, respectively, and both arms 20 and 22 are pivotally supported on a mold hinge pin 32. Pairs of toggle links 34 and 36 are provided between each of the rock shafts 24 and 26 respectively, and its associated lmold holder arm as best shown in FIG. 1. Each pair of toggle links 34 and 36 comprises a first link 33 having one end which is split as shown and clamped to the upper end portion of each rock shaft by a screw 35 and a pin 37. A second link 39 is pivotally connected at one end to the first link by a pin 41, and another pin 43 pivotally connects the opposite end of the second link 39 to one of the mold holder arms 20 or 22 as shown. In the closed position of the toggle link pairs, 34 and 36, they define movable knee portions which will ibe described in greater detail hereinbelow.

Referring now to FIGURE 2, the frame of the glassware forming machine is indicated generally at 38 with certain conventional components depicted therein in schematic fashion. Each of the rock shafts 24 and 26 is r0- tatably supported in a bearing block as indicated generally at 40, which bearing block is anchored to the frame 38 of the machine as by a plurality of machine screws indicated generally at 42. The lower end of the hinge pin 32 is non-rotatably supported in a boss 44 and the hinge pin 32 extends upwardly some distance beyond the upper ends of each of the rock shafts 24 and 26 as best shown in FIG. 2. Each of the mold holder arms is pivotally supported on the hinge pin 32 as described hereinabove. The bearing blocks 40, 40 and the boss 44 are integrally formed in a support bracket 46, which bracket comprises a generally flat horizontal base portion 48 which is attached to the machine frame as mentioned hereinabove. The support bracket 46 also includes web portions 50 and 52 which serve to further strengthen the bearing blocks 40, 40 for a purpose to be described hereinbelow.

In a conventional Hartford LS. type glassware forming machine, and also in a machine embodying the present invention, a rotary timing drum 60 having a plurality of camming buttons 62, 62 mounted around its periphery rotates about a generally horizontal axis as shown schematically in FIG. 2, in the direction `of the arrow 64 so that each of the buttons 62, 62 trips a valve lever (not shown) in a valve block or housing 66 to feed air under pressure, sequentially, to the various components of a section of the glassware forming machine. As represented schematically in FIG. 2, air under pressure is selectively transmitted to Vone or the other sides of a fluid motor 68, which motor is in turn linked to the lower ends of the rock shafts 24 and 26 by a rather complex linkage system which need not be described in detail herein, but which is represented by the numeral 70 in FIG. 2. As so constructed, the rock shafts 24 and 26 are pivoted angularly about their respective longitudinal axes for movement in opposite directions, as indicated by the arrows 28 and 30 of FIG. l, to open and close the blank mold sections a and 10b in timed relationship with movement of other components of the glassware forming machine.

In accordance with the present invention, an upright support post 72 is integrally provided in the support bracket 46 immediately behind and adjacent the hinge pin 32 and, generally intermediate each of the rock shaft bearing blocks 40, 40. As viewed in FIG. 2, the upright support post 72 can be seen to be quite thick in cross section throughout its length, and especially intermediate its lower and its upper ends so as to resist bending generally toward and away from the hinge pin 32.

In further accord with the present invention, an antideflection bracket, or tie bar 76, is provided between the upper end of the support post 72 and the upper end of the hinge pin 32, and means is provided for preadjusting the effective length of the tie bar 76 so that the hinge pin can be pre-stressed, or at least restrained against the stresses caused by closing movement of the mold holder arms, and especially those stresses resulting from operation of the booster units to be described.

As shown in the drawings, the means for pre-adjusting the effective length of the tie bar 76 comprises an eccentric bushing 78 best shown in FIG. 3, which bushing has an inner bore 77 for rotation about the upper end portion of the hinge pin 32, and which bushing also has an outer cylindrical surface which is at least initially rotatably received in an opening in the tie bar 76. The bushing bore 77 and its cylindrical outer surface are non-concentric so that rotation of the bushing causes relative movement between the tie bar 76 and the upper end of the hinge pin 32. Preferably, and as best shown in FIGS. 1 and 2, the upper end of the bushing has a wrench head 79 which can be conveniently rotated with a conventional wrench in order to achieve the foregoing adjustments.

In further accord with the present invention, means is provided for releasably clamping the bushing 78 in a particular angular orientation corresponding to a desired pre-stress of the hinge pin 32. As shown, said means cornprises a slot 82 for closing the same and thereby clamping the bushing 78 to the tie bar 76. A roll pin 86 is driven through the tie bar and through the side wall of the bushing 78 as best shown in FIG. 3 in order to further restrain the bushing 78 against inadvertent rotation in the tie bar 76.

The opposite end of the tie bar 76 is releasably clamped to the upper end of the support post 72 as best shown in FIG. 2. A key 88 extends generally perpendicularly with respect to the direction of pre-load stress to be exerted, and as shown the key 88 is received in a suitable slot dened in part in the upper end of the support post 72 and in part in the underside of the tie bar 76. The rear face of the key 88 is inclined slightly to receive a similarly shaped forwardly facing surface in the tie bar defined portion of the keyway. These surfaces comprise locating surfaces which are accurately machined in order to preposition the tie bar opening relative to the outer cylindrical surface of the eccentric bushing 78 just described.

Referring now to FIG. 4, it will be seen that the key 88 is actually in two sections, each of which is anchored to the support post by a suitable screw 90. Suitable means is provided for holding the tie bar downwardly in engagement with the upper end of the support post 72 so that the abovedescribed force is reacted by these key sections 88, 88. As shown in FIG. 4, said means comprises a threaded stud 92 which is anchored to the support post 72 by lock nuts 94, 94. The stud 92 extends upwardly through an opening dened by the inner ends of each of the key sections 88, 88 and then through an opening in the tie bar 76 so that a wing nut 96 can be threaded on the stud 92 to clamp the left-hand or rear end of the tie bar 76 while the above-described adjustments are made to the eccentric bushing 78 at its right-hand or forward end.

In further accord with the present invention, booster means is provided for increasing the closing force exerted on the mold closing linkage, at a point adjacent to the mold sections 10a and 10b. More particularly, a pair of iluid motors and 102 are arranged on either side of the support post 72 so that reciprocable portions, or parts thereof, are adapted to forcibly engage the knee portions of each of the toggle links 34 and 36, respectively. Each iuid motor, as for example the motor 102 shown in horizontal section in FIG. 1, comprises a xed part or housing mounted to the support post by means of a bracket portion 104 best shown in FIG. 2 which bracket portion is secured to the post 72 by a plurality of screws 106, 106. Each of the fluid motors further comprises a movable part, or piston 108, having an associated `actuating rod extending forwardly through an opening in the housing for engaging a cam plate 112 which is secured to the bifurcations of the link 33 by the screws 114, 114.

The air driven pistons 108, 108 are movable to the active positions shown by air pressure delivered to the motors through a manifold line 116 best shown in FIG. 2. The manifold extends through a valve 118 to be described hereinbelow so that air under pressure can be directed through a pair of relatively short lines 120, 120 to the interior of the motor housings as shown in FIG. 1. The air pressure manifold line 116 communicates with the valve block 66 as indicated schematically in FIG. 2 so that each of the fluid motors 100 and 102 are driven to the position shown in timed relationship with movement of the primary mold closing cylinder 68. The closing force achieved at the mold itself can thus be boosted by these pneumatic motors.

Each of the pneumatic motors further includes a return spring 121 best shown in FIG. 1 so that when air under pressure is no longer delivered to the pneumatic motors the piston 108 is retracted and the conventional mold opening mechanism employed to split the partible mold sections 10a and 10b as described in the Ingle patent. During retraction of the piston 108, air in the pneumatic motor is vented to the atmosphere through the valve 118 which will now be described.

As best shown in FIG. 5, the exhaust Valve 118 comprises a rectangular housing having a top vent opening 122 through which the air in each of the iiuid motors 100 and 102 is vented during return movement of its associated piston 108. The air pressure line 116 communicates with the interior of the housing 118 through a bottom opening and suitable internal passageways are provided in the housing so that air under pressure is delivered to each of the lines 120, 120 for actuation of the pneumatic motors 100 and 102. A one-way check valve 124 is provided in each of these passageways so that return movement of the piston 108 in each of the pneumatic motors 100 and 102 does not tend to pressurize the supply line 116 and hinder retraction of the rods 110, 110. A gravitybiased vent valve element 126 is slidably received in a vertical bore in the valve housing and s adapted to seal the vent opening 122 whenever pressure is supplied through the line 116. When the valve block A66 shuts off air pressure in the pressure line 116, the vent valve element 126 drops onto 4a pin 127 to the position shown in broken lines in FIG. 5 by gravity and also from reduced air pressure so that air in each of the motors 100 and 102 can be vented through the lines 120, 120 and thence outwardly through the vent opening 122. A bafe plate 128 is preferably provided in spaced relation above the vent opening 122 to decrease the force of the Vent airstream during operation of the machine.

In conclusion then it will be seen that each of the booster motors 100 and 102 is adapted to exert a forwardly directed force against the knee portion of each associated pair of toggle links 34 and 36 during closing movements of the mold to boost the closing force. Also, the mold hinge pin 32 is prestressed in a direction opposite to the force exerted thereon by the booster assisted closing of the mold halves, the prestress being eiiected by the adjustable length tie bar 76 connecting the upper end of said hinge pin 32 to the vertical support post 72. Thus, an improved mold closing linkage is provided for use with relatively large molds where internal friction in the conventional mold closing linkage precludes positive closing and setting of the partible mold sections a and 10b against the high pressure within the molds. The operation of the booster motors 100 and 102 is controlled by the same timing drum 60 which is used to drive the conventional mold opening and closing mechanism so that the operation of these booster motors can be closely timed in relation to the operation of the conventional mold opening and closing cylinder 68.

I claim:

1. 11n a glassware forming machine having partible mold sections mounted on mold holder arms which are pivotally supported on a common upright hinge pin iixed at its lower end in the machine frame, and having a pair of rock shafts rotatably supported in said frame and adapted to being driven through a predetermined angular displacement in timed relation with other components of said machine, the improvement comprising a pair of toggle links connecting said rock shafts to said mold holder arms for opening and closing movement of said mold sections in response to angular movement of said rock shafts, an upright support post fixed in said machine frame adjacent said hinge pin, a tie bar having one end connected to said support post and an opposite end connected to the upper end portion of said hinge pin to prevent hinge pin deiiection, a pair of ud motors each of which has a xed part mounted on said frame and a movable part adapted to forcibly engage the respective knee portions of each of said toggle link pairs to increase the closing force on the mold sections.

2. The combination as set forth in claim 1 and further characterized by means for preadjusting the effective length of said tie bar so that said hinge pin can be prestressed to counteract stresses which are created upon engagement between said toggle links and said movable fluid motor parts.

3. The combination as set forth in claim 2 wherein said means for preadjusting the effective length of said tie bar comprises an eccentric bushing having an inner bore for rotatably receiving the upper end portion of said hinge pin and an outer cylindrical surface which is rotatably received in an opening in said tie bar, said bore and said cylindrical surface being non-concentric so that ro tation of said bushing causes relative movement between said tie bar and said hinge pin.

4. The combination as set forth in claim 3 and further characterized by means for releasably clamping said bushing in a particular angular orientation corresponding to a desired stress of said hinge pin.

5. The combination as set forth in claim 4 wherein said clamping means comprises a slot defined in said tie bar and extending transversely across the tie bar opening for rotatably receiving said eccentric bushing, and a screw extending through said tie bar and across said slot for closing the same and thereby clamping said bushing to said tie bar.

6. The combination as set forth in claim 4 wherein said support post and said tie bar cooperate to define a keyway extending generally perpendicularly with respect to the direction of the force associated with said prestressing, a key in said keyway, and means for securing said tie bar to said support post so that said pre-stressing force is reacted by said key.

7. The combination as set forth in claim 1 wherein the movable part of each of said fluid motors comprises an air driven piston and associated rod, and wherein an air manifold line supplies air under pressure to both of said pistons simultaneously, and wherein each of said toggle link pairs includes one link carried by its associated rock shaft and a second link pivotally connected at one end to said one link and at its opposite end to a mold holder arm, and a cam plate attached to said one link, said cam plate being engageable by said piston rod.

8. The combination as set forth in claim 7 and further characterized by biasing means inside each of said air motors for returning said pistons to inactive positions when said air pressure is not supplied, and a common valve for venting said air motors when said air pressure is not supplied.

References Cited UNITED STATES PATENTS 2,052,343 8/1936 Du Bois 65-359 X 2,748,536 6/ 1956 Allen 65-360 2,307,563 1/ 1943 Bridges 65-360 3,199,970 8/ 1965 Dierksheide 65-360 S. LEON BASHORE, Primary Examiner A. D. KELLOGG, Assistant Examiner U.S. Cl. X.R. 

